Triple-action press



April 24, 1951 R. w. GLAsNER ET AL 2,550,062

TRIPLE ACTION PRESS Filed Jan. 2o, 195o 9 sheets-sheet 1 April 249 1951 R. W. GLASNER ET AL TRIPLE ACTION PRESS Filed Jan. 2o, 195o 9 sheets-sheet 2 April 24, l95 R. W. GLASNER ET AL.

TRIPLE ACTION PRESS 9 Sheets-Sheet 3 Filed Jan. 20, 1950 WH. Inflhl 0 7 ,v Y 11 l 5 0MM @NE 655 Mm i; Wi @Pf MM 1 R. W. GLASNER ET AL.

TRIPLE ACTION PRESS 9 Sheets-Sheet 4 Filed Jan. 20, 1950 April 24, 1951 R. w. GLASNER ET AL 2,550,062

TRIPLE ACTION PRESS Filed Jan. 20, 1950 9 Sheets-Sheet 5 April 24, 1951 R. w. GLASNER ET AL 2,550,062

TRIPLE ACTION PRESS Filed Jan. 2o, 195o 9 sheets-sheet e April 24, 1951 R. w. GLASNER ET AL TRIPLE ACTION PRESS 9 Sheets-Sheet '7 Filed Jan. 20, 1950 mamy/Mmmm a. @o 0 u 5 2 0 7 W a 4 N Z u MH fri/1.1 j y w //m M @M r f J .f 9 5 j 6 9 7 2 o 3 fw 7 rr. f iifllldrllravlllllminfnlllttllnnifilll r|\ .,/l\\\\\\\\ \\A m X l@ W 5 i T n/v .1 J w 7 7 x r 4. 5 y o 7 w Q Q a w w April 24, 1951 R. w. GLAsNl-:R ET AL 2,550,062

TRIPLE ACTION PRESS 9 Sheets-Sheei 8 |||||lllllllwlIII\JIIIIII|IIVN Filed Jan. 20, 1950 April 24, 1951 R. W. GLASNER ET AL TRIPLE ACTION PRESS Filed Jan. 20, 1950 9 Shee'ts-Sheet 9 EGQEEs v ONE CYCLE Patented pr. 24, 1.951

JohansengOak Park, Ill., assignors to 'Clearing MachineCorporation, Chicago,vIll., a corporation ofv Illinois' Application January 2o, 195o, serial No. 139,617

comms: 01. naa-38)- IThis invention 'relates' in'g'eheral'to presses' 'of th'e type forforming; shaping or'v drawing sheetA metal, and particularly"t'me'chanically'operated presses for' performing' such functions. specifically, theinvention relates to mechanically operated presses of these-called 'triple actio'n type; as distirlguishedr from' the double" action' into position by the outer'orfclamping slide. The

lower or secondary draw 'slide is'positio'ned below the she'et'metal blank andis'moved'upwardly to perform a second drawing' or shaping action on the' blankafter the upper' draw slide' has acted thereon. In someA instances the partsmay be reversed so'that theflower slide acts rst, in which casef it becomes thefir'st'action slide.

slide which performsv 'th seconddraw" isv herein referred to as the secondary slide.

Thesep'resent f pressesl `haveipro'ven` veryY satisfactoryfingeneral, butthey have the disadvan-v tage' in -that they-are unable to vproduce the def sired production quantity principally because the number voli-operatingcycles per period oftimev is limited. Thefinadequacy of the numberY of operations Vor 'operating cycles per period of time-re tards the productionlineand, therefore; limits'- and prevents rapid vproduction. 'Ihe-reasons'ior the lack of-more rapid'- production because of the limited number' `of cycles? of operation within Va given time limit are due to the-'co'nstruotion,4 p'o'- sition and arrangementA of parts.' These-prior mechanical presses are ordinarily operatedby a linkageV arrangement connected with the -upper or primaryclraw'slide and` the lower or secondary draw slide is operated b'yafcr'ank or-ecce'ntric arrangement connected-therewith, In some cases the secondary draw slide is Ydriven'by a separate and independentdrive means, and the forming or drawing of the sheet'metal must-be consistent withVL the type-'of sheet' metal which' is now available.

The ,present available sheet steel ordinarily has* afg safe '-maximumx drawing-1 or i' owing i speed of More In 'any' event the slide which" performs the lvfirst draw 'is herein'- referred ltoea's the-primary slide, and the' lfus minute.

2, ab'out eet'p'er minnte. `Therefore,A the actual" speed* at which sheetV steel "may be drawn *isy lima ite'd' by' the safe' InaXim'umA permissiblev flowing or Vdraw speed ofthe metall.' Shouldth'e speed at" which themetalis jdrawnh'ey increased above `this'v upperliniitj the sheet'nietal will'fracture, break",` or 'otherwise preventa' propermetal draw; unless th draw is'relatively. shallow. Conventional mechanical crank operated-metal f presses' 'tll'er'eforev have" Vthe#disadvantageA in tha-tj thethrwof the'crankdetermines Athe 4depth oi' the draw of the'primary draw slideA or;` conversely, the depthv of' the' draw tok be performe'don the metal' determinesthe throw" of" the craintA to bietused.v For'v example, should-a metal'dra'wy of 24'; inches "berequired, the'vertical movementof then upper draw slide must'beat least 48 Airl'ch'esplusl an'v additional amountjtoi permit' then iinish'edu drawn metal or" article toI be withdrziwn fromrv they dies;` The primaryv drawy slidey must` move' 24 j inchesfrom the point it rst engagesIv theiblankl in order to lnishthe 24-inch draw: The draw slideu must then be'raised 24 inches to withdrawv it"from Vthefnished piece where it will be at the i same point where vthe YmetalVN drawing operation began: It'iis 'then'neces'sary" to raise Ythe;n draw y slide anY additional 24 inches soitliat the 'firiish'edj or drawn article maybewithdrawn-from thel press.` Of` course, there must Abe more" than 4 84 inches overeall travel'so thatthenished drawn piecemay be withdrawi'il freely' from 'the' press. In *anyA event, the' primary drawV slide must have at leasta iS-"inch travel or movement fora-244:- inch metal draw;` l

The crank'which operates adraw slide tope'r`` e form a 24''inch draw 'must'necessarily haveA at"4 least a 48-'inch'stroke,'and inasmuch as th'e'crank rotates Aand the crank connections operate in van`v arc, rthe actual peripheral length ofthe arc about which the crank/connection travels, or the crank throw, will be the diameter of the arc times pi:-` (4 3 1416), or approximately 12:5664`feetY per Since'th'e"drawingtspeed of sheeti-steel as' used'fat 'the present time 'v is' about^60 'feet' perl minute', the'movem'en'tv of' the 'crank'imustibe'lim it'e'd' in speed 'according'`-to"l themaximiimpermis'' sible drawspeedf'of the# metal, viz.` ll'fieet'y per f" minute. Thereforeto" effect a 24-inch' drawl" the'Tj peripheral rotatif/e3 speed* of the` cranl willW4 125664"fee-tperf'miriuteg; Becausefth production on a triple action press of metal,

drawn articles without exceeding the actual and safe maximum drawing speed of the metal, the metal drawing operation still being limited by the conventional type of sheet steel available which has a safe maximumpermissible drawing speed of approximately 60 feet per minute.

The primary object of the present invention, therefore, is to maintain the present ,drawing speed to which sheet steel is limited, but to proy vide a new system of operating mechanism in a triple action press to eiect a greater number of cycles of operation over a given period of time.

A further objectv of the invention is the provision of new and improved mechanism for a triple action press whereby the operating mechanisms for all of the slides are interconnected and correlated to effect simultaneous travel of the clamping slide and primary draw slide to the point of clamping position of the clamping slide, then to maintain the outer or clamping slide in its clamping position while the primary draw slide is moved independently to effect the draw, then to cause the primary draw slide to dwell while the secondary draw slide effects its draw, thereafter to withdraw both the primary and secondary draw slides from operation, and finally to move the clamping and primary draw slides simultaneously to their original positions.

A further object of the invention is the pro- -vision of new and improved means for operating minute over the conventional mechanically opl er'ated triple action presses.

`A still further object of the invention is the provision of new and improved mechanism for operating a mechanical triple action press so as to increase the number of cycles of operation per minute for both the primary and secondary draw slides and still not exceed the maximum drawing speed of the metal blank, and so as to permit the bed of the press to be maintained at its usual lower position with the primary draw slide and clamping slide operating above the press bed, whereby the nished and completed or drawn article may be withdrawn from the press inthe usual manner without inverting the dies. Y

A still further object of the invention is the provision of new and improved mechanism for operating the primary and secondary draw slides of a mechanical triple action press so as to increase the number of operating cycles per minute but reducing the usual effective vertical movement of the primary draw slide by eliminating the ordinary crank throw employed in connection with the conventional crank-operated draw slide and yet permit the primary drawv slide to dwell while the secondary draw slide is performing. its operation on the metal blank.

Still another object of the invention resides 4 in the arrangement of the mechanisms for operating both the primary and secondary draw slides and the clamping slide by the attachment of the slide operating mechanisms to a common movable member instead of attaching the mechanisms for the clamping and primary draw slides to a stationary cross head such as is usually e1nployed and located in the 'crown of the press.

Another object of the invention resides in the provision of a plurality of interconnected, properly correlated and synchronized elements cooperating with both the clamping and primary draw slides to effect faster reciprocation of both slides simultaneously to a given point and then reducing the speed of the primary draw slide to effect the first drawing or forming operation in accordance with limits not to exceed the maximum permissible drawing speed of the metal being drawn, and thereafter causing a dwell of the primary draw slide while the secondary draw slide performs its drawing operation also at a speed not exceeding the actual drawing speed of the metal. Moreover Athere is provided a mechanical interlock between the connecting links for the clamping slide and the primary draw slide to permit a dwell of the primary draw slide at the proper time and prevent the slides from operating out of proper timed relationship with each other. Y

Other objects and advantages of the invention will become apparent from reading the following description taken in conjunction with the accompanying drawings, in which:v

Fig. 1 is a detailed longitudinal vertical sece tional view of the press of the present invention showing the clamping slide and the primary draw slide at their extreme upper positions and illustrating the secondary draw slide in its lowermost position, certain of the parts being broken away for the sake of clarity, and the linkage mechanism for actuating the primary draw slide being shown in elevation;

Fig. 2 is a view similar to Fig. 1 but showing the clamping slide in clamping position against the blank and the primary draw Slide about to begin its drawing action, the secondary draw slide being shown in an intermediate position' and the complete linkage mechanism for the clamping slide being shown in detailed elevation; Y v

Fig. 3 is a view-similar to Figs. 1 and 2 butY showing the primary draw slide at the complel tion of its drawing action and the secondary draw slide about to begin its drawing operation, the linkage mechanism for the primary draw slide being shown in detailed elevation;

Fig. 4 is a vertical sectional view through the press showing the clamping slide and the primary draw slide still in position at the end of the rst draw and showing the secondary draw slide at the completion of its drawing operation, the linkage mechanisms for the clamping slide and the primaryl draw slide being omitted from this View for the sake of clarity, and the crank construction together with the eccentric straps which operate the secondary draw slide being shown in detailed elevation;

Fig. 5 isa horizontal sectional View along the plane of line 5 5 of Fig. l;

Fig. 6 is a fragmentary Vvertical sectional view taken along the plane of line 6 6 of Fig. 4;

Fig. 7 is a fragmentary detailed perspective view of interconnecting linkage between the clamping slide and the primary draw slide and illustrating the manner in Which the clamping gether;

Fig. 8- is a detailed horizontal sectional view takenalong the plane of line 8 8 of Fig. 3;

Fig. 9 is a fragmentary vertical sectional View taken along the plane of line 9-9 of Fig. 2;

Fig. 10 is a fragmentary vertical sectional view taken along the plane of line IIJ--Ill of Figs. 2 and 3;

Fig. 11 is a top plan View of the press;

Fig. 12 is a developed sectional plan viewof theprimary draw slide linkage, the linkage being-V spread out in a straight line to show the various linkage parts and the manner in whichv they are connected; and

Fig. 13 is a cyclograph of moion curve showing the operation of the three slides in the tripley action press of the present invention.

The triple action mechanical press herein shown for the purpose of'illustrating the present invention includes a main supporting structure generally indicated by the numeral I. Thisy supporting structure has as a part thereof a base or bed 2 reinforced by strengthening walls or webs 3 (Figs. l to 4). The press also includes an outer or clamping slide 4 and a primary draw slide 5 having a plurality of strengthening webs vintegral therewith. At the bottom of the press there is provided a secondary draw slide 1' having a plurality of strengthening webs 8. The outer or clamping slide 4 at the upper part of the press is commonly called the first action slide since it is the iirst to move and perform its operation of clamping the metal blank in place to have the drawing operations performedv thereon. The primary draw slide 5 maybe referred to as the second action slide, since its drawing operation takes place immediately after the blank has beenvclamped in place, although it performs the first or primary drawing or forming action on the blank. The secondary draw slide 1 may he termed the third action slide, since it is the last to perform its drawingl action on the metal blank.

A link 9 is connected to the outer or clamping slide at each corner of the press and is caused to-reciprocate the clamping slide 4 at predeter mined intervals by a suitable linkage mechanism to be described in more detail hereinafter. A link IB is connected with the primary draw slide 5 at each corner of the press and causes reciprocation of the primary draw slide through the medium of a second linkage mechanism alsor to be described in more detail hereinafter. Ecfx. centric Straps or links II mounted on cranks* are connected with the secondary draw slide 1 and cause operation of the secondary draw slide in a predetermined timed sequence with respect to the clamping and primary draw slides.

Referring now more particularly to Fig. 5, there is illustrated the manner in which a single motor is caused toactuate all three slides in the triple action press of the present invention. A main drive shaft I2 is supported in suitable bearings carried by a part of the main supporting structure I. This main drive shaft I2 is driven in any -suitable manner such as by belts I3 trained over a pulley I4 on the shaft I2 and over a pulley I5 on the motor shaft IG of an electric motor I1.

The main drive shaft I2 carries a gear i3 which meshes with and drives a gear I9 on a transverseA driven shaft 2U, this shaft 20 being journaled in suitable bearings inthe -walls ofthe mainframe;

Gili'.

its

sha-ft 22.

` mesh at the opposite side of the press and. arer mounted on the respectivedriven shafts 20 and 22. Drive gears 25, 26, 21, 28, 29 and3 are fixed to the rotatable driven shaft 20. Similar. drive gears'. 3l, 32, 33, 34, 35 and 36 are mounted on the driven shaft 22. Rotation of themotor shaft I6 thereforefcauses the driven shafts 20.,.and 22 together with the gears mounted thereon, to rotate simultaneously, but in opposite directions, .the shaft .20. and-gears leand 23at the ends thereof rotating; in a clockwise direction and the shaft 22.With.its. gears 2| and 24rotating in acounterclockwise: directionY as shown by the directional arrows, for.A example, in Fig. 2. A main split shaft31 is suit.- ably mountedwithin theframe of the machine in close relation to and 'parallel' with. the driven shaft 20. As will be presently seen, the shaft..31` is split to accommodate a crank at the center of the press to actuate the secondary drawslide. This split shaft 31 has clamping slide bull gears:

. 33 and 39 mounted near the ends of the shaft,

the-bull gears 33 and 39 .onthe main shaft 31 in a counterclockwise direction.

A second main split shaft-.Maat theA opposite 1 side of the machine is located adjacent the driven shaft. 22 and is parallel therewith. Fig. 5 illusi trates the mounting for the split shaft 40to accommodate the crank for the .secondary draw.l slide, this construction being identical with that. forthe main shaft 3'! at the opposite side/of the machine. The split main shaft'lll, which is sta- .l tionary, carries rotatably mounted outer slide bull gears 4l and 42'whlch are located near the outer ends of the shaft and which mesh respectively with the gears 3| and 36 on the driven The shaft 22, being drivenin a counterclockwise direction, will rotate the gears 4I and 42 in a clockwise direction. y

Therouter slide bull gears 38 and 39 on thefmain split shaft 3i have outer slide eccentrics 43 and 44, respectively, which are rotatably mounted onpthe shaft 31. The bull gears 4i and 42 on the second main split shaft 40 carryeccentrics 45 and 43', respectively., which rare rotatably mounted on the shaft 4U. The eccentrics 13,A 44, 45Vand i6 carryeccentric straps 41, 43, 49 andv A, 5d respectively which operate certain clamping slide linkage mechanisms` 5I (Fig. 2) for the clamping slide connection llinks 9 of the outer or clamping slide 4. There is one such clamping slide linkage mechanism 5l and one such clamping slide connection link 9 ateach of the fourl corners of the press, making ka total of four such` clamping slide linkage mechanisms 5I and four such clamping slide connection links 3 to recipro` cate the outer or cla'mpingslide 4 vertically in.

the main machine frame I.

The main split shaft 31 has primary draw slide Vbull gears 52 and 53 rotatably mounted thereon .spectively on the driven shaft 25 and are driven thereby in a counterclockwise direction.

The main split shaft 40 carries rotatably mounted primary draw slide bull gears 54 and 55 which are positioned between the outer: slide gears 4I Vand 42. These f-gearsf"54an'd 55fmeshf-v with gears 32 and 35 respectively on the driven shaft-22 and are driven thereby in a clockwise direction.

The bull gears 52 and 53 on the main split shaft 31 and the bull gears 54 and 55 on the split shaft 49 drive eccentrics 56, 51, 58 and 59 respectively which are rotatably mounted on the Yrespective main shafts 31 and 48. The eccentrics 56, 51, 58 and 59 drive eccentric straps 68, 6|, 62 and 63 respectively which operate certain primary draw slide linkage mechanisms 64 (Fig. 1) for the primary draw slide connection links I9 of the primary draw slide 5. There is one such primary draw slide linkage mechanism 64 and one such primary draw slide connection link I at each of the four corners of the upper draw slide, making a total of four such upper draw slide linkage mechanisms 64 and four such primary draw slide connection links I0 to reciprocate the primary draw slide vertically in the main frame l.

The main split shaft 31 also has secondary draw slide bull gears 65 and 66 rotatably mounted thereon at the inner ends of the split portions thereof. These gears 65 and 66 are connected together by a crank pin 61. The gears 65 and 66 mesh with gears 21 and 28 on the driven shaft 20 and are therefore driven in a counterclockwise direction. The split portions of main shaft 40 have secondary draw slide bull gears 68 and 69 rotatably mounted thereon, these gears 68 and 69 being connected together by a crank pin 10. These gears 68 and 69 mesh with gears 33 and 34 respectively on the driven shaft 22, whereby the gears 68 and 69 may be caused to rotate in a clockwise direction. The crank pins 61 and 18 carry the eccentric straps and are connected at their upper ends to the secondary draw slide 1 (Figs. 1 to 5) Outeior Clamping Slide 4 and Linkage Mechanism 51 Therouter or clamping slide 4, as illustrated'in Figs. 1, 2 and 3, is operated by certain linkage mechanism5| which is clearly shown in Figs. 2 and '1. The operation of this linkage mechanism 5| causes a vertical reciprocation of the clamping slide connection links 9 to reciprocate the outer or clamping slide 4. Each linkage mechanism 5| (Figs. 2 and r1) for each link 9 comprises a bell crank 1l pivotally mounted on a stationary rocker pin or stud shaft 12. One end of the bell crank 1| is pivotally connected at 13 to a clamping slide eccentricV strap, such as 5|) Y and 48 in Fig. 2. The other end of bell crank 1| is pivotally connected at 14 to a link 15. The link 15is pivoted at 16 to one arm of a bell crank 11 which is mounted on a stationary stud shaft 18. The other arm of bell crank 11 is pivotally connected at 19 to one end `of a link 86. The other end of link 86 is pivotally connected at 8| to one arm of a bell crank 82. The bell crank 82 is pivotally mounted on a stationary shaft 83 and has the other arm thereof pivotally connected at 84 to one end of a connecting link 85. The other end of the connecting link 85 is pivotally connected at 86 to one arm of a bell crank 81 which is pivotally mounted on a stationary shaft 88 and rocks about this shaft 88. Theother arm of bell crank 81 is pivotally connected'to the lower endl of a clamping slide connection link 9 by means of a clamping slide connection link pin 89` (Figs. 2 and 10). The upper end of each clamping slide connection link 9 is pivotally mounted on a pivot pin 96'carried by the outer or clamping slide 4 (Figs. 2 and 9).

The linkage mechanisms 5| for each of the connecting links 9, from the point where the link 9 connects to the bell crank 81 up to the point 13 where the bell crank 1| pivotally connects to a clamping slide eccentric strap, are identical, there being a linkage mechanism 5| connected to each of the eccentric straps 41, 48, 46 and 50 to operate the respective clamping slide connecting links 9 (Fig. 5). The linkage mechanisms 5| are identical in construction, there being two such mechanisms on the right-hand side of the press and two such mechanisms 5l on the lefthand side of the press (Fig. 5). The positioning of the right and left-hand vlinkage mechanisms 5| is clearly shown in Fig. 2. These right and left-hand-linkage mechanisms 5| are duplicated, there being one pair at the front of the press and one pair at the rear (Fig. 5). Since these linkage mechanisms 5| are all identical and since one of the mechanisms has been described in connection with one clamping slide connecting link 9, this description will suffice for the other linkage mechanisms 5l which operate the clamping slide connecting links 9.

Operation of the main drive shaft |2 rotates the driven shafts '26 and 22 through the medium of the gears I9 and 2| which, in turn, rotate gears 25 and 3U and their eccentrics 43 and 44 on the splitshaft 31. shaft 22 will also cause driven gears 3| and 36 to rotate on that shaft as Well as gears 4| and 42 and their eccentrics 45 and 46 on split shaft 40. The eccentric straps 41, 48, 49 and 56, being connected through the linkage mechanisms 5| to the clamping slide Aconnecting links 9, operate the bell cranks 1|, links 15, bell cranks 11, links 88, bell cranks 82, links 85, and bell cranks 81. These bell cranks 81 are thereby caused to oscillate on their shafts 88. This oscillatory movement of the bell cranks 81 causes the connecting links 9, and consequently the clamping slide 4, to move vertically. ThisY clamping slide 4 moves from the uppermost position shown in Fig. 1 to the clamping position shown in Figs. 2 and 3 and then back again to. theY original initial positionY shown in Fig. 1, whereby one full cycle of operation is completed. i

Primary Draw Slide 5 and Linkage Mechanism 64 The eccentric straps 6D and 6| on shaft 31 andv the eccentric straps 62 and 63 on shaft 46 operate thel primary draw slide connecting Vlinks I9 to reciprocatey the primary draw side 5 in upward and downward directions (Figs. 1 and 3). The primary draw slide 5 is suitably guided in guides carried by the outer or clamping slide 4 and is adapted to reciprocate in and with respect tothe outer or clamping-slide. Each of the eccentric straps 66, 6|, 62 and 63 operates a connecting link I6 through the medium of a primary draw slide linkage mechanism 64. There is a primary draw slide connection link Il) at each of the corners of the primary draw slide and suitably attached nected at 96 to one arm of a bell crank 91 `rotat'- The rotation of driven;

ably mounted on' astud shaft 18`. The other arm of bell'crank 9T is pivotally connected at 95 to one end of a link IBB. v The other end of link I U is pivotally connected at IIJI to one arm of a bell crank lever |52 rotatably mounted on a stad shaft 8ST. The other arm of bell crank IGZ is pivotally connected at I4 to one end of a link |55. The other end of link is pivctally connected at ISS to one arm of alv bell crank in the form of an arcuate member IBI pivotally mounted for rotation intermediate the ends thereof by the same pin 89' which connects the clamping slide connecting link 9 with thebell crank 3l of the clamping slidelinkage mechanism. The other arm of bell crank IS'I is pivotally connected at IGS to the lower end of a primary draw slide connecting link I. The connecting link IIJ is pivotally attached to the primary draw slide 5 at itsV upper end by means of a connecting pin les (Figs. 1, s and e). p

The primary draw slidelinkage mechanism 64 for each primary draw slide connecting link Ii), from the point where the lower end thereofl pivotally connects with the bell crank IIll to the point 93 where the' bell crank 9i connects with a corresponding primary draw slide eccentric strap, is identical, there being a linkage mechanism 64 connected to each eccentric strap 65, 6I, 62 and 63 to operatey a'respe'ctive primary draw slide connecting linke It!Y (Figs. l, 3 and 5). The linkage mechanisms G4 are identical in construction, there being two such linkage mechariisms-64 on the right-hand side of the press and two such linkage mechanisms on the left-hand side of the press (Fig. 5). These rightand lefthand primary draw slide linkage mechanisms 54 as shownin Figs. l and 3 are duplicated7 there being a pair at thefront'and'a pair at the rear, making a total of four such linkage mechanisms corresponding to the four eccentric straps 65, 5I, 62 and 65 as shown in Fig. 5. The size, shape and construction as well as the pivotal connections for the various parts forming the linkage mechanisms 64, from the point H38 where the primary draw slide connectingv links I5 connect with the bell crank II to the point 93 Where the bell crank 9i pivotally connects with the eccentric strap, are identicalj therefore, sinceA the primary draw slide linkage mechanism has been described Withrespect to one primary draw slide connecting link I it is unnecessary to repeat the description with respect to the other linkage mechanisms for each of the other connecting links IS.

The'rotation of the gears 52, 53, 54`and 55 and their-eccentrics 55, 5l, 58 and'55 on the respectiveushafts 3l and 45 will cause operation of all of the fourprimary draw slide linkage mechanisms 64. The' primary draw slide mechanismsr 64 operate the primary draw slidev connecting links Iii which in turn causevertical'reciprocatin'of the primary draw slide'5.

Fig. 1 shows the primary 4draw slide 5 at its uppermost position. Fig. 2A shows the position of the primary draw slide just before the beginning ofthe metal drawingY operation and at the time the clamping slide 4 is'at its dwell and clamping position. Fig; 3A shows the' primary draw slide 5 at the completionof its metal- ,drawing operation; The' primary draw slide 5 therefore is causedto reciprocate Yirointhe'z position shown in Fig. 1 to thev positionv shown in Fig. 3' and then back'to the positionfsh'own in'Fig 1 to complete oneVv cycle of operation. The primary' drawl slide 5l and clampingy slide' iar'e f drivenby the driven shafts' 25 and 22 whereby boththe primary draw 4 and the linkage mechanism 64 for the primary draw slide 5 is such that both slides 4 and 5 will move downwardly from the initial upper positions shown in Fig. l to a position where the clamping slide 4 will clamp a workpiece III] r forming or 4drawing operation.

against a part of a lower female die Il I mounted on the press bed 2. The primary draw slide 5 carries a male forming die II2 which is adapted to cooperate with the female die III during the' The linkage mechanisms 5I and 64 are so constructed and arranged that there will be a dwell of the clamping slide 4 when the clamping slide clampingly engages the metal blank I Il) and during the time the primary draw slide 5 operates to perform the metal drawing operation. After the clamping slide has engaged andy clamped the metal and while the clamping slide is dwelling', the primary draw slide continues downwardly to the position of Fig. 3 to effect the metal drawing operation.

Unlike the double action press, however, wherein the primary draw slide may begin its return upward movement immediately after the drawing operation, the triple action press of the pres'- ent invention requires that the primary drawslide 5 dwell for a short period of time after its drawing operation to permit the secondary draw slide to Lperform its drawing operationY onthe metal blank. The necessity for this dwell of the primary draw slide'5 after .its ,drawing operation requires a considerablydifferent linkage mechanism arrangement for actuating the primary draw slide than would otherwise be necessary if the primary draw slide could return immediately after its drawing operation Aas in a double action press. y

It is desirable and necessary that there be a proper dwellof the clamping slide 4 to permit the workpieceV IIE! to be securely and rigidly held in place on the lower die I I I while the metal drawing operation is being performed by'both the primary and secondary draw slides. It is also necessary and desirable that the primary and secondary draw slides move' away in their respectivedirections from the drawn metal before movement of the clamping slide 4 so as to free the dies and the finished article, whereupon the clamping slide and the primary dr-aw slide move upwardly together while the secondary draw slide moves downwardly to permit the nished workpiece to be removed from between the dies'.

The secondary draw slide? rI-he secondary draw slide 'I has a forming die I I3 mounted thereon. The actuatingmechanism'V for thesecondary draw slide 'I must be properly timed in synchronism with the operations of the clamping slide 4 and primary draw slide 5 so that the forming die I I3 performsv its drawing operation on the metal blank I I immediately after the drawing operation of the primary draw slide 5v and during the dwell thereof. The gears 65 and 65 mounted on the inner ends of the splitA tric 'strap I I is pivotally connected by means of ai Y '11 pin Ila on the secondary draw slide 1 (Figs. 1;2, 3 and 6).

The gears 21 and 28 on the driven shaft 20 drive the gears 65 and 66 at the same rate of speed and in the same direction as the primary draw slide gears 52 and 53 and the outer slide gears 38 and 39. The crank 61 willcause eccentric movement of str-ap I I in timed relation with the movement of the primary draw slide eccentric straps 60 and 6| and with the clamping slide eccentric straps 41 and 48. Likewise, the gears 33 and 34 on driven shaft 22 will drive gears 68 and 69 and crank connected therebetween in the same direction and at the same rate of speed as the primary draw slide gears and eccentric straps 54, 55, 62 and 63, respectively, and as the clamping slide gears and eccentric straps 4|, 42, 49 and 50, respectively.

The straps are located on each side of the machine and move by means of the respective cranks 61 and V10 so as to reciprocate the secondary draw slide 1 upwardly and downwardly.

Bell crank construction for linkage mechanisms 51 and 64 'Ihe various bell cranks which are included in the clamping slide linkage mechanism 5| must be strong, durable and rigid, and must also be capable of withstanding hard usage and overcoming stresses' and strains. This is also true for the bell cranks which effect operation of the primary draw slide 5. A practical arrangement for constructing these bell cranks is shown in Fig. 7.

The bell crank 81 which has connected thereto the connecting link 9for operating the clamping slide 4 is composed of two sets of spaced suitable shaped plates, one set being indicated by the nu-V merals ||4 and ||5 and the other set being indicated by the numerals ||6 and ||1.- These spaced plates I I4, ||5, ||6 and ||1 which are. shaped to form bell cranks are integrally connected together by a central hollow hub I I8. This hollow hub V|18 is mounted on the stub shaft 88 for pivotal movement with respect thereto. i The connecting link 9 which operates the clamping slide 4 is arranged between the spaced side plates ||4 and ||5 and is pivotally connected thereto by means of the pivot pin 89. The link or arm 85 is likewise arranged between the spaced plates ||4 and ||5 and is pivotally'connected thereto by means of the pivot pin 86.

The bell cranks 82, 11 and '.'I are all similarly constructed, the bell crank 82 consisting of the spaced properly shaped plates I I 9 and |20. These spaced plates I I9 and |20 are integrally connected by the central hollow hub |2| which receives the stub shaft 83, thereby allowing the spaced plates forming the bell crank 82 to pivot thereon. Bell crank 11 consists of the spaced properly shaped plates |22v and |23 integrally connected together by the hollow hub |24 which receives the stub shaft 18 and thereby allows the bell crank 11 to have pivotal movement thereon. Bell crank 1| embodies the spaced suitably shaped plates |25 and |26 integrally connected by the hollow hub |21 which receives the shaft 12 and permits the bell crank 1| to have pivotal movement thereon.

'I'he eccentric strap 50 is received at one end thereof between the spaced plates |25 and |26 and is pivotally connected thereto by pivot pin 13. The intermediate links 15, 80 and 85 are all received between the spaced plates of the adjacent bell cranks and are pivotally connected thereto by the pivot pins as clearly shown in Fig. '1. Operation of the driving gear 42 (Figs. 2 and 12 5) will drive theeccentric strap 50 to reciprocate bell crank 81 about shaft 88 as a pivot through the medium of the linkage mechanism 5|.

As previously pointed out, there are four such linkage mechanisms 5| to operate each of the four connecting links 9 for reciprocating the clamping slide 4. The bell cranks just described are identical in construction for each of the four sets of linkage mechanisms 5|.

The arcuate bell crank |01 associated with each of the four linkage mechanisms 64 is also clearly illustrated in Fig. '1 and embodies the two spaced suitably shaped plates |28 and |29. 'I'hese plates 28 and |29 are provided With inwardly extending bosses |30 and |3| (Fig. 8) which form spacing members to insure proper spacement of the plates. Each bell crank |01 embodying the spaced plates |28A and |29 is mounted for pivotal movement on the stub shaft 89 and between the spaced plates 6 and ||1 on the bell crank 81. Thus it will be seen that rotation of bell crank 81 on the clamping slide 4 will include a rotation of the spaced plates l|6 and ||1 connected to theV bell crank |01, whereupon suitable movement will be imparted to bell crank |01 independently of the eccentric strap associated with the primary draw slide linkage mechanism 64.

The other bell cranks |02, 91 and 9| compris-V ing the linkage mechanism 64 are all similarly constructed and consist of spaced suitably shaped plates, the bell crank |02 being shown clearly in Fig. '7. The bell crank |02 includes the spaced plates |32 and |33 integrally connected by the hollow hub |34 which receives the stub shaft 83 on which the bell crank 82 of the clamping slide linkage mechanism is also mounted. Y

The connecting link l0 for the primary draw slide 5 has its lower end arranged between the spaced plates |28 and |29 of bell crank |01 and is connected thereto by the pivot pin |08. The link |05 has one end thereof received between the opposite ends of the spaced plates |28 and |29 and its other end received between the spaced plates |32 and |33 of bell crank |02. Y K Y The other bell cranks 91 and 9| arealso formed of spaced suitably shaped plates in the same manner as bell Vcrank |02 and receive the links |00 and 95 therebetween. Bell crank 91 of the primary draw slide linkage mechanism 64 is mounted for pivotal movement on shaft 18 which is the same shaft on which bell crank 11 of the clamping slide linkage mechanism 5| is mounted. Bell crank 9| of the primary drawY slide linkage mechanism 64 is mounted for pivotal movement onshaft 12 which is the same shaft on which bell crank 1| of the clamping slide linkage mechanism 5| is mounted. The eccentric straps 60, 6|, 62 and 63 have their outer ends each received between the spaced plates of the adjacent bell crank 9|. Each eccentric strap connected to a bell crank 9| operates the linkage mechanism of the primary draw slide in Vsuch a way as to cause the Vdrawing action of this slide and then to permit a dwell of the primary draw slide while the secondary draw slide performs its drawing operation upon the workpiece.

The various bell cranks of the primary draw slide linkage mechanism are arranged and interconnected with the bell crank 81 of the clamping slide linkage mechanism so that when the primary draw slide and clamping slide are both in their uppermost positions, as shown in Fig. 1, and then begin their respective downward movements, they will move downwardly together.. At this pOint 0,1 initial downward movement. the

not be caused "to vmove thereby. The eccentric Astraps 41, 48, 49 and 50'which actuate the clamping 'slide linkage mechanism 5| will then cause links v9 Vrapidly downwardly. At the same time, downward movement of the spaced plates ||6 and I (Fig. 7) will move each bell crank |07 downwardly to effect rapid downward movement of'theprimary draw slide .5 through the connectvinglink IU. After the clamping slide has securely rclamped the workpiece in'position, then the eccentric straps BD, 6|, 62 and 63 which operate the primary draw slide linkage mechanism 64 cause continued movement of bell cranks |01 Awhile bell vcranks 81 dwell. This action continues the downward movement o'f each .connecting link 10, thereby causing the primary draw slide ,5 to ef- 'fect its drawing action. The arrangement of the bell cranks in each linkage mechanism 6.4 for the primary drawslide is so Varranged that after the drawing action has been completed, the primary draw slide will dwell during the Work or drawing `stroke of the secondary draw slide 1.

The eccentric straps Il, which are mounted on the cranks 61 and 15.! and are driven by gears mounted on Athe split shafts 40, are connected directly `to the secondary draw slide without any linkage-mechanism intervening. This construction permits the secondary idraw slide to be elevated vand lowered vquickly while both the .clamping slide and the primary draw .slide are dwelling. rIfhe .eccentric straps are so arranged on their respective .shafts iso `as to .begin upward movement while Vthe clamping slide and primary draw slide .are moving downwardly. `At the end of the working `str okeof the primary draw slide, the secondary :draw slide will then be in position to -begin .its working stroke upwardly. The secondary draw slide then .effects its drawing voperation and immediately moves downwardly. After the secondary drawslide has lbegun ,its downward movement, the vprimary draw slide and clamping slide will move upwardly..

.and will Areturn to their uppermost -positions shown in Fig. 1. At the conclusion of the upward Vtravel of the clamping .slide and primary draw .slide and of the .downward -travel of the secondary draw slide, `a new metal blank ||.|J is [inserted vin position `and'another cycle of operation is repeated.

It has .been .found that the construction employed vin the slide operating mechanisms em- .'bodied yin the present .invention will permit a considerable .number .of cycles of operation to kbe performed withina given period of time. The number .of actual operating cycles per unit ,of time is considerably greater than is possible with mechanical triple action presses employ- .ing the crank construction as .commonly used.

This is 'true even though the .primary and secondary draw slides do not perform the actual drawing .operation-of the metal at .any increased speed. The increased number 4of cycles is obtained by simultaneously and rapidly -moving the 'clamping slide and primary -draw slide whenever the primary and secondary draw slides are not effecting their respective drawing actions. Such operation is possible because the respective pairs of linkage mechanisms 5I and 64 are tied together or interconnected and because these linkage mechanisms are designed in a manner such that they will cause the clamping and primary draw slides to move relatively .rapidly toward -rotation of bell cranks 8l to move the connecting Jand :awayi'from ithe `workpiece `whenever the latter `isnot being drawn by the primary and secondary -draw slides. The clamping slide is positioned slightly .below the primary draw slide in their uppermost positions so that as these slidesmove ldownwardly together, the clamping slide will contact the workpiece rst and perform its vclamping .function 'thereon just before the prifmary draw slide contacts the workpiece .and .begins yits drawing operation.

The -secondary-draw slide in conventional' triple action presses does not ordinarily begin its Aupward movement until the work has been .clamped in place ,by .the clamping slide. This requires considerable dwell by both the clamping `slide and the primary draw slide which is time consuming -and is avoided in the present invention where the secondary draw slide begins its upward movement at substantially the same time that thefclamping Vand primary draw slides begin their downward movement.

This increase of the number of cycles per .given period of time is `possible in the present Iinvention by rthe arrangement of the linkage mechanisms which operate the slides and the manner in'whichfthey are `tied together as heretofore explained.

It Vshould be 'brought 4out that inthe conventional triple action'press, 'for a drawing depth of the primary draw slide of 24 inches, there must be an .overall travel of the crank of more `than-ei feet, because the primary draw slide'must move downwardly 2 'feet .to perform the draw'- ing operation and `then move more than 4 feet `upwardly `to Ipermit the completed 'Work to be withdrawn frombetween the dies. For va 4-foot overall movement, :there would have to be a .peripheral movement of the crank of 4 times pi, which would be a total peripheral movement Jof 12.5664 feet. Inasmuch as the maximum drawing speed of the present conventional sheet steel now ynormally used is 60 feet per minute, `there could 4be only about 4.77 cycles of operation per minute. Should Vthe speed of operation .oi Yan ordinary crank operating the slides of a mechanical triple laction press be increased, it vwould exceed the metal flowing or drawing action of the sheet steel. This increased speed would cause -th'e sheet steel to rupture, crank or otherwise become deformed. In any event, the 'speed of the draw may never exceed the drawing capabilities mately 60 feet per minute, the elasticity and .other characteristics of the sheet metal being limited. The present construction permits the 'number of' complete cycles of operation to be rincreased because the speed of travel of both the clamping slide andthe primary draw slide, and also the speed of travel of the secondary .draw slide, vcan be increased without exceeding the draw limitof the metal to be formed. The invention therefore permits the metal to be drawn at the proper speed, but allowsthe number of cycles per minute of the machine to be increased over that Anumber permissable in conventional presses. A press embodying the present design and construction can almost double the output or production over Apresent mechanical crank- .operated triple action presses.

Fig. 13 is a cyclograph ora motion curve il- `lustrating the timing and operation of the three slides. The curve indicated by the numeral 4 represents the motion curve of the clamping slide 4. The curve indicated fat -5 v.represents the of the metal which is approxirmotion of the primary draw slide 5, and the numeral 1 indicates the motion curve for the secondary draw slide 1. It will be noted that the clamping slide 4 and primary draw slide 5 move downwardly simultaneously, but the lprimary draw slide 5 moves downwardly at a greater rate of speed than the clamping slide-4. This results in the clamping action of the clamping slide 4 taking place only a fraction of a second before the primary draw slide begins its drawing operation as indicated by the point A in Fig. 13. The secondary draw slide 1 moves upwardly at the same time that the downward movement of the clamping slide 4 and primary draw slide 5 takes place. The secondary draw slide 1 begins its drawing operation at substantially the moment the primary draw slide 5 finishes its drawing operation at the point B in Fig. 13. The' secondary draw slide 1 begins its return downward movement immediately after effecting the draw, During the drawing action of the secondary draw slide, the clamping slide 4 dwells during the cycle from point A to point C. During this action of the secondary slide 1, the primary draw slide also dwells from point B to point D. As soon as Athe secondary draw slide 1 has returned downwardly the distance ofthe draw, the primary draw slide 5 will begin its upward movement and a fraction of a second thereafter the clamping slide 4 begins its upward movement.

It will thus be evident that while the actual drawing operation of the draw slides consumes about the same length of time as is customary in conventional mechanical triple action presses,`

the movement of all of the slides before and after the drawing operation is much faster, whereby all of the slides are caused to return to their respective upper and lower open positions and thereafter return tothe operating positions thereof in 'considerably less time than is ordinarily required in the usual mechanical triple action press. This motion curve establishes that the drawing operation is accomplished within the limits of the drawing capabilities of the metal, but the number of cycles of operation per minute is considerably increased over the number possible in conventional triple action presses.

Guides for clamping slide 4 The clamping slide 4 is guided for vertical reciprocation in the main frame or supporting structure The main frame is provided with guide members |35 at the four corners thereof, as clearly shown in Fig. ll. Each guide member |35 is rigidly and adjustably secured to a part of the main frame and includes an inwardly eX- tending leg |36 terminating in an inner inclined face 31. The face 31 of each guide member |35 is adapted to cooperate with an inclined face |38 on a projection |39 on the cross members |48 of the clamping slide 4. The cooperating and aligned faces |31 and |38 on the members |36 and |39, respectively, prevent shifting of the clamping slide 4 within the main frame and maintain the outer or clamping slide in proper vertical sliding position with respect to the main frame I. The guide faces |31 on the members |36 Yand the guide faces |38 on the members |39 of the clamping slide preferably extend from the top to the bottom of the main frame and the clamping slide 4, respectively. The clamping slide 4 is therefore properly guided within the frame of the press.

Guides for primary draw slide 5 The primary draw slide 5 is mounted within the confines of the clamping slide 4. The clamping slide is provided with a central opening |4| through which the primary draw slide 5 operates.

The primary draw slide 5 is guided by cooperating guides on the primary draw slide and the clamping slide. End shifting of the primary draw slide with respect to the clamping slide is prevented by the abutting engagement of guide strips or slides |42 and |43 on the primary draw slide and clamping slide, respectively, at both ends thereof. Front-to-rear shifting of the primary draw slide with respect to the clamping slide is prevented by the guides |39 on the clamping slide which terminate in guiding faces |44 engaging guide strips |45 on the primary draw slide, four such pairs of guiding members |44 and |45 being provided, there being two pairs of guides at the rear and two pairs of guides at the front, all as clearly shown in Fig. 1l. The primary draw slide therefore is guided within the clamping slide by the cooperating engagement of Ythe members |42 and |43 and the members |44V Adjustments for primary draw slide and Y clamping slide The primary draw slide and the clamping slide are adapted to be shifted closer to or farther away from the lower die which is mounted 'on the bed of the press according to the movement these slides are to have with respect to the particular drawing or metal forming operation. The primary draw slide and clamping slide may each be automatically adjusted according to the character of work being drawn and the depth of the drawing. The adjustment of each of the slides is accomplished by shifting the slides vertically with respect to the slide connection links 9 and The primary draw slide 5 is adapted to be adjusted vertically by an electric motor |46 mounted on an upper surface of the primary draw slide 5. The shaft of the motor |46 carries a pinion |4511 which engages a gear |41 on a drive shaft |48 (Fig. ll). This drive shaft |48 carries a drive gear |49 at each end thereof and these gears |49 mesh with gears |50 spaced on opposite sides of each of the gears |49. The gears |55 are each fixed to a shaft which carries and drives a bevel gear |5|, there being a bevel gear |5| for each of the primary draw slide connecting links Ill (Figs. 9 and 11). -Each of the bevel gears |5| meshes with a bevel gear |52.y Each bevel gear |52 is fixedly secured to a nut |53 (Fig. w9) which is held against vertical movement by a retaining member |54. The gear 52 and nut |53 are, however, free to rotate. The nut |53 is threadedly engaged with the threads on an adjusting screw |55. Each adjusting screw |55 is provided with spaced jaws |55 at its lower end, which jaws receive the upper end of a connecting link I0. The pin |59 passes through the upper Vend of each connecting link and through the spaced jaws |56, thereby securing the adjusting screw |55 to its adjacent connecting link |ll. Therefore as the shaft of the motor |45 rotates, the bevel gears |52 and their companion nuts |53 will also rotate, but inasmuch as vertical movement of the nuts |53 is prevented by the retaining members |54 xed to the top of the primary draw slide 5, the adjusting screw |55 will be trans- 17 lated vertically and cause the primary draw slide to be translated downwardly or upwardly, depending upon the direction of rotation of the nuts |53. The four bevel gears |52 are all rotated at the same time during the rotation of shaft |48 by means of the motor |46. Therefore the same amount of movement will be effected with regard to each of the connecting links l5 whereby the primary draw slide will be Vtranslated vertically.

The means for effecting the vertical adjustment of the clamping slide 4 is accomplished in the same manner as the yprimary draw slide adjustment. Such means for effecting the clamping slide adjustment comprises worm gears |51 (Figs. 9 and 11) which also carry nuts |56 -x'ed to the top of the clamping slide by retaining members |59. Adjustment screws |66 threadedly engage each nut |58. Each of v'these screws |60 is connected to a link 9 by means of av pin 93 passing through the lower bifurcated end of screw |66 and through an opening inthe upper end of link 9. Each worm gear |51 is driven by a wor-in |62 mounted on a shaft |63. The inner end of each shaftA |63 carries a pinion |64 in mesh with a gear |65 on a shaft |66. There is one shaft |66 at each side of the machine rand each such shaft carries a gear |65 on -eachend thereof. Thus there arefour such gears |65 each meshing with a gear |64 driven by a shaft |63.

The opposite end ofeach shaft |63 carries a bevel gear |61 in mesh with another bevel gear |68 at each end of a transverse shaft |69. There is a transverse shaft |69v at each end of the machine which has mounted thereon at Aeach end a bevel gear |68. Therefore there are four suchbevel gears |68 each meshing' with a bevel gear |61 on the outer end of a shaft |63. At one end of the machine' one vof the shafts |69 carries/a gear |10 driven by a pinion on the 'motor shaft of motor |1|. Operation of the motor ill thereforecauses each worm |62to driveeach worm gear |57 rotating the nut |58 and causing 'upward or downward'shifting movement of each of the screws Y| 66 and the clamping 'slide '4 through the vconnecting links 6 carried thereby. AThe operation of all of the -gears being from the -single motor will cause the gears to be `'rotated exactly thes'ame amount thereby causing all parts of the clamping slide to be moved upwardly 'or downwardly "the same distance and at the same rate.

The secondary draw slide l needs no such adjusting mechanism associated therewith because the length of draw of the secondary draw slide c 'an be adjusted bythe size and shape of the die thereon or by shimming or building up the bottorn of the die.

Any suitable clutch mechanism may be employed between the motor Il and main drive shaft shown in Fig. 5. Only a single clutch is required or necessary tocause the clamping slide vand both the primary and secondary 'draw slides to be operat'ed from a singlesource 'of power which is the main drive motor Il. Separate clutches for the separate slides therefore are unnecessary, there being but one motor and one clutch provided for operating and controlling the operation of all three slides and the mechanism which operates them.

i v12e-suine The invention provides a mechanically operated press particularly of the triple action type rin which` is embodied a clamping slide, a primary draw slide and a secondary draw slide. Linkage mechanisms are provided "in the press for first 18 moving the clamping slide into clamping engagemerit with a metal blank or workpiece. Other linkage mechanisms are provided for moving the primary drawslide so as te draw `part of the workpiece or `blank into a female die while the 'said workpiece is being clamped against the die by means of the clamping slide. Eccentric straps are connected directly with the secondary draw slide and with -a crank mechanism forl causing afdrawing operation to be performed on the Workpiece or blank lby the secondary draw slide after the primary draw slide has completed its operation. The linkage mechanisms for the clamping slide and primary draw slide are tied together in a manner such that the `primary draw slide will move downwardly 'with the clamping slide until the clamping slide engages the metal blank or workpiece. The primar-y draw slides moves through a greater distance than the clamping slide, and the linkage mechanisms are Vtied together in such a way as to move the lprimary draw slide downwardly with the clamping sli'd'e but more rapidly than the clamping slide so that the drawing operation of the yprimary draw slide will commence `at substantially `the moment the clamping slideis `in clamping position. The linkage mechanisms for the primary draw slide operate to cause a drawing operation to be performed on the metal workpiece While the linkage mechanisms `for theclamping slide cause said clamping slide to dwell in clamping position against the workpiece or blank.

The resulting increased production without increasing the drawing speed of the primary and secondary draw slides is obtained through the linkage mechanisms of the primary draw slide and the clamping slide plus the manner in which these linkage mechanisms are tied together. lThe clamping slide is caused to reciprocate by A.the linkage mechanisms 5|. 'Ihe primary draw slide is caused to reciprocate independently of the clamping slide by means of the linkage mecha'- nisms 64. Each pin 86 V(Figs. `l and 2) connects the linkage mechanism 6E with the linkage mechanism 5| so that rotation of bell crank 8l will cause reciprocation of both the clamping'slide 4 and primary draw slide' simultaneously. The additional Arotation of bell crank |67 during this movement of bell crank `8l ralso causes reciprocation 'of `theprimary draw slide 5 therebyincreasing the speed of the movement of the primary draw slide 5 at all times other than dring the lactual drawing operation. The linkage mechanism 64 is so arranged th'at'the primary draw slide 5 is caused to dwell during the drawing operation 'of the secondary'draw slide l.

Present triple actionv vpresses 'wherein the clamping vslide and 'primary draw s'lide 'are operated by a crank causethese slides to reciprocate at 'substantially the s'a'me rate of 'speed 'duri'ng the 'non-drawing movement thereof as vduring the drawing operation. The speed 'of 'drawing can not be increased beyond the limit of the metal to be formed; 'therefore the increased speed of the slides both before and after the drawing operation due to the linkage mechanisms "w'ill result in less vtime consumed from' the `time`the blank is inserted on the lower die until theiinished article isl removed from'the machine.

rlhe invention also provides new and novel acljustment mechanisms whereby the clamping 'slide and primary draw slide may be adjustedvertically and *whereby these slides may be -adjusted independently of each other. Such "adjusting mechanisms are provided in the press of the 'pres- 19' ent invention for the purpose of setting or adjusting the relative positions of the primary draw slide and the clamping slide for various kinds of metal drawing operations.

It is' desirable that the bed of thepress and the forming die, as well as the linkage mechanisms which operate the slides, be located at or near the bottom of the press with the clamping Slide and primary draw slide located at or near the top of the press. The invention, however, contemplates thereversal of these parts so that the stationary bed will be above the clamping slide and the secondary draw slide and the linkage mechanisms willbe in the crown of the press.

The present invention has been illustrated herein so that the primary draw slide is the second action slide andY the secondary draw slide is the third action slide. The invention, however, contemplates further that the linkage mechanisms be so arranged that the secondary draw slide be the second action slide and the primary draw slide be the third action slide.

Changes may be made in the form, construction and arrangement of'parts from that disclosed hereinwithout departing in any `Way from the spirit of the invention or sacrificing any of the attendant advantages thereof, provided, however, that such changes fall within the scope of the claims appended hereto.

The-invention is hereby claimed'as follows:

1. A mechanical press of the triple action type comprising a frame structure including a bed, a clamp slide, a primary draw slide, -a secondary draw slide, a clamp slide eccentric, a primary draw slide eccentric and a secondary draw slide eccentric, all of said eccentrics being mounted on a common drive shaft, a bell crank pivotally mounted on the frame structure, a'plurality of rocker arms pivotally mounted on the frame structure, a set of links interconnecting said rocker arms, said links and said rocker arms interconnecting the clamp slide eccentric with said bel1"crank,a clamp slide link connecting said bell crank with said clamp slide, said clamp slide eccentric, bell crank, rocker'arms and links being so arranged and coordinated with respect to each other that operation of the: clamp slide eccentric will bring the clamp slide to clamping positionand then cause the'clamp slide to dwell, a second bell crank pivotally mounted on the rst said bell crank at a point thereon spaced from the pivot of said first bell crank to the frame structure, a second pluralityV of rocker arms pivotally mounted on the frame structure, a second set of links interconnecting said second pluralityv of rocker arms, said second plurality of rocker arms and said second set of links interconnecting the primary draw slide eccentric with one arm of said second bell crank, a draw slidelink connecting the other arm of said second bell crank With said primary draw slide, said primary drawv slide eccentric, second bell crank, and second plurality of rocker arms and links being so arranged and coordinated with respect to each other that operation ofthe primary draw slide eccentric will cause said primary draw slide to perform a drawing operation and then dwell, and means connecting said secondary draw slide eccentric with said secondary draw slide, said eccentrics being angularly offset from each other so that operation of the clamp slide .eccentric will move both the clamp slide and the primary draw slide toward the bed bringing the clamp slide into c lamping'position, theeiiective operation of the dwell of the clamp slide and the primary draw slide.

2. A mechanical press of the triple action type comprising a frame structure including a bed, a clamp slide, a primary draw slide, a secondary draw slide, a clamp slide eccentric, a primary draw slide eccentric and a secondary draw slide eccentric, all of said eccentrics being mounted on i.; a common drive shaft, a rocker member pivotally mounted on the frame structure, a plurality of rocker arms pivotally mounted on the frame structure, a set of links interconnecting said rocker arms, said links and said rocker arms interconnecting the clamp slide eccentric with said rocker member, a clamp slide link connecting said rocker member With said clamp slide, said clamp slide eccentric, rocker member, rocker arms and links being so arranged and coordinated with respect to each other that loperation of the clamp slide eccentric will bring the clamp slide to clamping position and then cause the clamp slide to dwell, a second rocker member pivotally mounted on the rst said rocker member at a point thereon spaced from the pivot of said rst rocker member to the frame structure, a second plurality of rocker arms pivotally mounted on the frame structure, a second set of links interconnecting said second plurality of rocker arms, said second plurality of rocker arms and said second set of links interconnecting the primary draw slide eccentric with said second rocker member, a draw slide link connecting said second rocker member With said primary draw slide, said primary draw slide' eccentric, secondY rocker member, and second plurality of rocker arms and links being so arranged and coordinated with respect to each other that operation of the primary draw slide eccentric will cause said primary draw slide to perform a drawing operation and then dwell, and means connecting said secondary draW slide eccentric with said secondary draw slide, said eccentrics being angularly offset from each other so that operation of the clamp slide eccentric will move both the clamp slide and the primary draw slide toward the bed bringing the clamp slide into clamping position, the eiective operation of the primary draw slide eccentric to effect the drawingv operation of the primary draw slide will occur during ,the dwell of the clamp slide, and so that the effective operation of the secondary draw slide'V eccentric to eifect the drawing operation of the secondary dravv slide will occur during the dwell of lthe clamp slide and the primary draw slide.

3. A mechanical press of the triple action typeV comprising a frame structure including a bed, a clamp slide, a primary draw slide, a secondary draw slide, a clamp slide eccentric, Aa primary draw slidee'ccentric'and a secondary draw slide` links and said rocker arms interconnecting the clamp slide eccentric Vwith said rocker member, a

clamp slide linkgconnecting said rocker member: withsaid clampslide, said clamp slide eccentric,l

rocker member, rocker arms andY links being so 21y arranged and coordinated with respect to each other that operation of the clamp slide eccentric will bring the clamp slide to clamping position and then cause the clamp slide to dwell, a second rocker membel` pivotally mounted on the nrst said rocker member at a point thereon spaced from the pivot of said first rocker member to the frame structure, a second plurality of rocker arms pivotally mounted on the frame structure, a second set of links interconnecting said second plurality of rocker arms, said second plurality of rocker arms and said second set of links' interconnecting the primary draw slide eccentric with said second rocker member, a draw slide link connecting said second rocker member with said primary draw slide, said primary draw slide eccentric, second rocker member, and second plurality of rocker arms and links being so arranged and coordinated with respect to each other that operation of the primary draw slide eccentric will cause said primary draw slide to perform a drawing operation and then dwell, and means connecting said secondary draw slide eccentric with said secondary draw slide7 said eccentrics being maintained in a predetermined angular relationship from each other so that operation of the clamp slide eccentric will move both the clamp slide and the primary draw slide toward the bed bringing the clamp slide into clamping position, the effective operation of the primary draw slide eccentric to effect the drawing operation of the primary drav/ slide will occur during the dwell of the clamp slide, and so that the effective operation of the secondary draw slide eccentric to effect the drawing operation of the secondary draw slide will occur during the dwell of the clamp slide and the primary draw slide.

4. A mechanical press of the triple action type comprising a frame structure including a bed, a clamp slide, a primary draw slide, a secondary draw slide, a clamp slide eccentric, a primary draw slide eccentric and a secondary draw slide eccentric, common drive means for all of said eccentrics, a rocker member pivotally mounted on the frame structure, linkage means interconnecting the clamp slide eccentric with said rocker member, at least one of the links in said linkage means being pivotally mounted on the frame structure, a clamp slide link interconnecting said rocker member with said clamp slide, said clamp slide eccentric, rocker member, linkage means and clamp slide link being so arranged and coordinated with respect to each other that operation of the clamp slide eccentric will bring the clamp slide to clamping position and then cause the clamp slide to dwell, a second rocker member pivotally mounted on the rst said rocker member at a point thereon spaced from the pivot of said first rocker member to the frame structure, a second linkage means connecting said second rocker member to said primary draw slide eccentric, a draw slide link connecting said second rocker member with said primary draw slide, said primary draw slide eccentric, second rocker member, second linkage means and draw slide link being so arranged and coordinated with respect to each other that operation of the primary slide toward the bed bringing the clamp slidev into clamping position, the effective operation of' the primary draw slide leccentric to effect the drawing operation of the primary draw slide will occur during the dwell of the clamp slide, and so that the effective operation of the secondary draw slide eccentric to effect Vthe drawing operation of the secondary draw slide will occur during the dwell of the clamp slide and the lprimary draw slide. Y

5. A mechanical press of the triple action type comprising a frame structure including a bed, a clamp slide, a primary draw slide, a secondary drawy slide, a clamp slide eccentric, a primary draw slide eccentric and a secondary draw slide eccentric, common drive means for all of said eccentrics, a bell crank pivotally mounted on the frame structure, operating means connecting said clamp slide eccentric with said bell crank, a clamp slide link connecting said bell crank with said lclamp slide, said clamp slide eccentric, bell crank, operating means and clamp slide link being so arranged and coordinated with respect to each other that operation of the clamp slide eccentric will bring the clamp slide to clamping position and then cause the clamp slide to dwell, a second bell crank pivotally mounted on the rst said bell crank at a point thereon spaced from the pivot of said first bell crank to the frame structure, a second operating means connecting said second bell crank to said draw slide eccentric, a draw slide link connecting said second bell crank to said primary draw slide, said primary draw slide eccentric, second bell crank, second operating means and draw slide link being so arranged and coordinated with respect to each other that operation of the primary draw slide eccentric will cause said primary draw slide to perform a drawing operation and then dwell, and means connecting said secondary draw slide eccentric with said secondary draw slide, said eccentrics being maintained in a predetermined angular relationship from each other so that operation of the clamp slide eccentric will move both the clamp slide and the primary draw slide toward the bed bringing the clamp slide into clamping position, the effective operation of the primary draw slide eccentric to effect the drawing operation of the primary draw slide will occur during the dwell of the clamp slide, and so that the effective operation of the secondary draw slide eccentric to effect the drawing operation of the secondary draw slide will occur during the dwell of the clamp slide and the primary draw slide.

6. A mechanical press of the triple action type comprising a frame structure including a bed, a clamp slide, a primary draw slide, a secondary draw slide, a clamp slide eccentric, a primary draw slide eccentric and a secondary draw slide eccentric, drive means for all of said eccentrics, linkage means connecting said clamp slide eccentric with said clamp slide including a link pivotally mounted on the frame structure, and said linkage means being so arranged and coordinated that operation of the clamp slide eccentric will bring the clamp slide to clamping position and then cause the clamp slide to dwell, a second linkage means connecting said primary draw slide eccentric with said primary draw slide, including a link pivotally mounted on said first link at a point thereon spaced from the pivot of said rst link on the frame structure, said second linkage means being so arranged and coordinated that operation of the primary draw slide eccentric will cause said primary draw slide to perform a draw- 

